JP4821864B2 - Shift control device for automatic transmission mechanism - Google Patents

Description

  The present invention relates to a shift control device for an automatic transmission mechanism configured to control an engine speed by controlling a transmission ratio of the automatic transmission mechanism.

  In a driven state in which the engine is driven by power input from wheels such as when the vehicle is traveling at a reduced speed, friction of the engine and a mechanical hydraulic pump driven by the engine becomes a load, and so-called engine braking force is generated. However, a load generated by driving the mechanical hydraulic pump among the engine brake force may cause the engine brake force to be excessive. An example of reducing the load is described in Patent Document 1. . In the invention described in Patent Document 1, the hydraulic pressure is supplied to the pulley of the V-belt type continuously variable transmission mechanism that requires a relatively high pressure hydraulic pressure. The oil pump for high pressure that generates the hydraulic pressure of oil is used, and the hydraulic pressure of relatively low pressure may be used, but the hydraulic oil that requires a large amount of pressure oil and the supply of pressure oil to the fluid transmission device are driven by the engine It is configured to use a mechanical low pressure oil pump.

  Patent Document 2 discloses a line pressure circuit system (high hydraulic circuit) to which a relatively high pressure is supplied, and another circuit system (low pressure) that uses the oil pressure drained from the line pressure circuit system as a hydraulic source. A hydraulic circuit), the discharge pressure of an oil pump driven by the engine is supplied to the line pressure circuit system, and the hydraulic pressure reduced by the regulator valve is supplied to another circuit system (low hydraulic circuit) The invention has been described. Furthermore, Patent Document 3 describes an invention in which an oil pump is driven when an upshift is performed to reduce the gear ratio, and the engine speed is quickly reduced by the drive resistance of the oil pump. ing.

JP-A-3-134368 Japanese Patent Laid-Open No. 2004-316832 JP 7-280080 A

  According to the invention described in Patent Document 1 described above, since two types of oil pumps, a low pressure oil pump and a high pressure oil pump, are provided, each is suitable for a torque converter, a clutch, and a continuously variable transmission mechanism. Therefore, the oil pump driving torque can be reduced as a whole, and power loss and lack of hydraulic pressure can be prevented or suppressed. However, in the configuration described in Patent Document 1, when the surplus hydraulic pressure on the low hydraulic pressure side is regenerated to the accumulator on the high hydraulic circuit side, the mechanical low pressure oil driven by the engine when the vehicle decelerates or the like The engine braking force increases due to the (drive) load of the pump.

  According to the inventions described in Patent Documents 2 and 3, when the vehicle is traveling at a reduced speed, the engine and the oil pump driven by the engine receive the power input from the wheels. May increase unintentional deceleration and may deteriorate drivability.

  The present invention has been made paying attention to the technical problem described above, and ensures the previous driving state when the engine braking force increases due to the driving resistance of the mechanical hydraulic pump, for example, when the vehicle is decelerating. It is an object of the present invention to provide a shift control device for an automatic transmission mechanism that can be used.

In order to achieve the above object, an invention according to claim 1 is directed to an automatic transmission mechanism that changes the power generated by an engine, a mechanical hydraulic pump that is driven by the engine and generates a hydraulic pressure at a relatively low pressure, and A pressure accumulator that communicates with the mechanical hydraulic pump and accumulates at least a part of the hydraulic pressure generated by the mechanical hydraulic pump, and controls the speed ratio of the automatic transmission mechanism to control the rotational speed of the engine. in shift control system for an automatic transmission mechanism that is configured to perform control for changing the said automatic transmission mechanism is mounted on a vehicle comprises a continuously variable transmission mechanism the speed ratio can be set steplessly, the previous SL engine Driven state determination means for determining that the driven state is driven by traveling inertial force, etc., and detects that the pressure accumulation amount of the pressure accumulator is below a predetermined value The pressure accumulation amount detection means and the driven state judgment means determine that the engine is in a driven state, and the pressure accumulation amount detection means detects that the pressure accumulation amount of the pressure accumulator is equal to or less than a predetermined value. If it is, calculates a target pressure accumulation amount to be accumulated in the accumulator, further causes boosted hydraulic pressure generating pre Symbol mechanical hydraulic pump, at least a portion of the hydraulic generating the mechanical hydraulic pump the and accumulating execution means for accumulated in the accumulator, based on the previous SL the target accumulator amount calculated by accumulating execution means and the rotational speed of the engine at that time, the case where the accumulated until the target pressure accumulation amount with respect to the accumulator the machine and the driving resistance calculation means械式is generated by the hydraulic pump calculates the driving resistance of the mechanical hydraulic pump for applying braking force to the vehicle, the drive to And Appushifu DOO amount calculating means for calculating the speed ratio of the continuously variable speed change mechanism to decrease the rotation speed of the engine so as to reduce the braking force corresponding to been driven resistance calculated by the resistance calculation unit, the continuously variable transmission mechanism characterized in that the by the upshift to the gear ratio calculated by the speed ratio the up shift amount calculation means, and a a Ppushifuto execution means to reduce the braking force corresponding to the drive resistance of the mechanical hydraulic pump It is what.

According to a second aspect of the present invention, in the first aspect of the present invention, in the first aspect of the invention, the sudden braking determination means for determining that the vehicle is in a state of sudden braking, and the state in which the vehicle is suddenly braked When it is determined that the vehicle is suddenly braked by the upshift prohibiting means for prohibiting an upshift that relatively reduces the transmission ratio of the continuously variable transmission mechanism and the sudden braking determining means. When it is determined that there is a downshift executing means for relatively increasing the gear ratio of the continuously variable transmission mechanism, and the gear ratio of the continuously variable transmission mechanism is set to be relatively large by the downshift executing means. And a transmission ratio detecting means for detecting that the set transmission ratio is greater than or equal to a predetermined transmission ratio. That.

According to a third aspect of the present invention, in the first aspect of the invention, the driving state change frequency detecting means for detecting that the number of times the engine repeats the driving state and the driven state within a predetermined time is a predetermined number of times or more, An engine that detects that the rotational speed of the engine is equal to or lower than a rotational speed that can offset the drive resistance generated by the mechanical hydraulic pump by performing an upshift that relatively reduces the speed ratio of the continuously variable transmission mechanism. A rotational speed detection means, wherein the number of times the engine drive state and the driven state detected by the drive state change frequency detection means are repeated is a predetermined number of times or more and is detected by the pressure accumulation amount detection means Shifting of an automatic transmission mechanism characterized in that when the pressure accumulation amount of the pressure accumulator is larger than the predetermined value, hydraulic pressure is not accumulated in the pressure accumulator. A control device.

According to a fourth aspect of the present invention, in the first aspect of the invention, the continuously variable transmission mechanism is a belt type in which a groove width of a pulley around which the belt is wound is changed by hydraulically moving a movable sheave constituting the pulley. A speed change control device for an automatic speed change mechanism, which is a continuously variable speed change mechanism.

According to a fifth aspect of the present invention, in the second aspect of the invention, the downshift execution means sets the gear ratio of the continuously variable transmission mechanism to one of a gear ratio at which the vehicle can restart and a maximum gear ratio. A shift control apparatus for an automatic transmission mechanism that downshifts.

  According to the first aspect of the present invention, at least a part of the hydraulic pressure generated by the mechanical hydraulic pump driven by the engine is stored in the accumulator in a driven state in which the engine is driven by a traveling inertia force or the like. In this case, the upshift is performed by the upshift execution means so as to relatively reduce the gear ratio of the automatic transmission mechanism. Thus, according to the first aspect of the present invention, hydraulic regeneration can be performed when the engine is driven, and the speed ratio of the automatic transmission mechanism is controlled to be relatively small, thereby reducing the engine speed. Be made. Therefore, since the rotational speed of the mechanical hydraulic pump is reduced, it is possible to suppress or reduce an increase in engine braking force due to the drive resistance of the mechanical hydraulic pump that occurs when the hydraulic pressure is accumulated in the accumulator. Moreover, generation of excessive engine braking force can be suppressed or prevented, and drivability can be improved. In addition, since a drop in vehicle speed due to an excessive engine braking force can be suppressed or reduced, reacceleration is facilitated and fuel consumption can be improved.

Further, according to the invention billed to claim 1, since the automatic transmission mechanism is a continuously variable transmission mechanism capable of setting the gear ratio continuously, the rotational speed of the engine corresponding to the drive resistance of the mechanical hydraulic pump The gear ratio for reducing the minute can be set appropriately. Also, a continuously variable transmission mechanism when a mechanical hydraulic pump that accumulates pressure when the engine is driven is excessively driven by the rotational speed of the driven engine, causing excessive engine braking force. By controlling the speed ratio of the engine, the engine speed can be reduced by the engine speed that excessively drives the mechanical hydraulic pump. Therefore, excessive driving of the mechanical hydraulic pump when the engine is in a driven state and the hydraulic pressure is accumulated in the accumulator can be suppressed or reduced, and an increase in engine braking force can be suppressed or reduced. Further, the gear ratio of the continuously variable transmission mechanism, that is, the upshift amount is calculated so as to reduce the engine braking force (braking torque) corresponding to the driving resistance of the mechanical hydraulic pump that increases the engine braking force. The gear ratio of the continuously variable transmission mechanism is controlled to the gear ratio. Therefore, it is possible to suppress or prevent the generation of excessive engine braking force due to the drive resistance of the mechanical hydraulic pump when accumulating pressure.

According to the invention of claim 2, in addition to the effect similar to the effect of the invention of claim 1 , when the sudden braking determination means determines that the vehicle is suddenly braked, the accumulated pressure is increased. At the same time, the gear ratio of the continuously variable transmission mechanism is relatively increased, that is, downshifted. Therefore, when the pressure accumulation amount of the pressure accumulator is less than or equal to a predetermined value, the pressure is accumulated, and excessive engine braking force is generated by the drive resistance of the mechanical hydraulic pump accompanying the pressure accumulation and the downshift of the continuously variable transmission mechanism. Therefore, it is possible to secure the amount of pressure accumulation and increase the braking force of the vehicle. Further, since the speed ratio of the continuously variable transmission mechanism during sudden braking is downshifted to a predetermined gear ratio, can be obtained Bei recurrence proceeds after sudden braking, also a large gear ratio required at the time of re-starting Can be secured. Therefore, it is possible to increase the braking force when the vehicle is suddenly braked, and to ensure the hydraulic pressure and the gear ratio that are required when the vehicle is restarted, thereby facilitating the restart after sudden braking.

According to the invention of claim 3, in addition to the same effect as that of the invention of claim 1, the number of changes in which the engine repeats the driving state and the driven state within a predetermined time is a predetermined number of times, and When the pressure accumulation amount of the pressure accumulator is equal to or greater than a predetermined value, pressure accumulation by the mechanical hydraulic pump is not performed. Further, pressure accumulation by the mechanical hydraulic pump is not performed when the rotational speed of the engine is equal to or lower than the rotational speed at which the drive resistance of the mechanical hydraulic pump can be offset by upshifting. Therefore, when the engine frequently repeats the driving state and the driven state, the so-called excessive engine braking force caused by the mechanical hydraulic pump frequently occurs with the driving of the mechanical hydraulic pump that performs pressure accumulation. It can be suppressed or prevented. In addition, since excessive engine braking force can be suppressed or prevented, the conventional drive state can be ensured as much as possible, and the controllability of the vehicle speed can be improved.

According to the invention of claim 4, in addition to the same effect as that of the invention of claim 1 , the continuously variable transmission mechanism is a belt type continuously variable transmission that changes speed by changing the groove width of the pulley around which the belt is wound. Since it is a mechanism, the gear ratio can be set steplessly by changing the amount of pressure oil supplied to the movable sheave that is supplied with pressure oil and changes the groove width of the pulley. Therefore, the gear ratio can be appropriately set so as to reduce the braking torque corresponding to the driving resistance of the mechanical hydraulic pump.

According to the invention of claim 5, in addition to the effect similar to the effect of the invention of claim 2 , the downshift executing means is adapted to reset the speed ratio of the continuously variable transmission mechanism when the vehicle is suddenly braked. Increase the gear ratio to start or the maximum gear ratio. Therefore, it is possible to ensure the vehicle restart performance and facilitate the vehicle restart.

It is a flowchart which shows typically an example of control of the transmission control apparatus of the automatic transmission mechanism which concerns on this invention. It is a flowchart which shows typically the other example of control of the transmission control apparatus of the automatic transmission mechanism in this invention. It is a flowchart which shows typically the other example of control of the transmission control apparatus of the automatic transmission mechanism in this invention. It is a flowchart which shows typically the other example of control of the transmission control apparatus of the automatic transmission mechanism in this invention. 1 is a diagram schematically showing a configuration of a vehicle to which a shift control device for an automatic transmission mechanism according to the present invention can be applied.

  Next, the present invention will be described with reference to specific examples. The vehicle Ve to which the present invention can be applied is an internal combustion engine (hereinafter referred to as the engine 1) such as a gasoline engine or a diesel engine, or a hybrid vehicle Ve using the engine 1 and an electric motor in combination, and a machine driven by the engine 1 Type hydraulic pump, a pressure accumulator for accumulating pressure by supplying at least part of the hydraulic pressure generated by the mechanical hydraulic pump, and a speed ratio to control the rotational speed of the engine 1 The present invention can be applied to a shift control device for any vehicle Ve provided with the automatic transmission mechanism 2.

  FIG. 5 schematically shows the configuration of a vehicle Ve to which the present invention can be applied. The continuously variable transmission mechanism 2 mounted on the vehicle Ve shown in FIG. 5 is a conventionally known belt type, and a belt (not shown) is wound around the driving pulley 3 and the driven pulley 4 to rotate these pulleys 3. , 4, and the transmission ratio is changed by changing the belt winding radius of each pulley 3, 4. More specifically, each pulley 3, 4 includes each fixed sheave 3a, 4a and movable sheave 3b, 4b arranged so as to approach and separate from each fixed sheave 3a, 4a. V-shaped belt-wrapping grooves are formed between the fixed sheaves 3a and 4a and the movable sheaves 3b and 4b. The pulleys 3 and 4 are provided with hydraulic actuators 5 and 6 for moving the movable sheaves 3b and 4b back and forth in the direction of the axis thereof. Any one of these hydraulic actuators 5, 6, for example, the hydraulic actuator 6 in the driven pulley 4, is supplied with a hydraulic pressure that generates a clamping pressure with which the pulleys 3, 4 clamp the belt. The other of the hydraulic actuators 6, for example, the hydraulic actuator 5 in the drive pulley 3, is supplied with hydraulic pressure for changing the belt winding radius.

  On the input side or output side of the continuously variable transmission mechanism 2 is provided a C1 clutch 7 for transmitting and interrupting drive torque. The C1 clutch 7 is a clutch in which the transmission torque capacity is set according to the supplied hydraulic pressure, and is constituted by, for example, a wet multi-plate clutch. The continuously variable transmission mechanism 2 and the C1 clutch 7 transmit torque for traveling of the vehicle Ve and are set to a transmission torque capacity corresponding to the hydraulic pressure. The high hydraulic pressure corresponding to the torque is supplied to the 5, 6 and C1 clutches 7. Therefore, the continuously variable transmission mechanism 2 or its hydraulic actuators 5 and 6 and the C1 clutch 7 or its hydraulic chamber (not shown) supply high hydraulic pressure using an electric hydraulic pump 9 driven by an electric motor 8 as a hydraulic source. Forming part.

  On the other hand, the power transmission device including the continuously variable transmission mechanism 2 is provided with a torque converter (torque converter) 10 having a lock-up clutch (not shown). The configuration of the torque converter 10 is the same as that conventionally known. In the converter region where the rotational speed difference between the pump impeller and the turbine runner is large and the speed ratio is smaller than a predetermined value, a torque amplifying action occurs. In a coupling range where the rotational speed difference is small and the speed ratio is greater than a predetermined value, it is configured to function as a fluid coupling having no torque amplification effect. The lockup clutch is configured to directly connect a front cover integrated with a pump impeller as an input side member and a hub integrated with a turbine runner via a friction plate.

  An L / U control valve 11 is provided as a control valve for controlling the lock-up hydraulic pressure for bringing the friction plate into contact with the front cover and separating the friction plate. The L / U control valve 11 is used to control the direction in which the hydraulic pressure is supplied to the lock-up clutch and the pressure thereof. Therefore, the L / U control valve 11 is configured to operate at a relatively low hydraulic pressure. . The L / U control valve 11 is provided with a lockup engagement solenoid 12 for operating the L / U control valve 11 to engage the lockup clutch.

In the power transmission device including the continuously variable transmission mechanism 2 and the torque converter 10 described above, there are a lot of so-called sliding portions or heat generating portions such as bearings and bearings, and lubricating oil is supplied to these portions. Is configured to do. These lubricating parts 13 may be supplied with a required amount of lubricating oil even at a low pressure. Therefore, the lubrication unit 13 and the above-mentioned L / U control valve 11 or the torque converter 10 forms a low oil pressure supply unit for the mechanical hydraulic pump 14 and the hydraulic pressure source driven by the engine 1.

  Next, a configuration for supplying and discharging hydraulic pressure to and from the high hydraulic pressure supply unit and the low hydraulic pressure supply unit will be described. A pressure regulating valve 15 that regulates the hydraulic pressure driven by the engine 1 and discharged from the mechanical hydraulic pump 14 to a predetermined pressure is provided. The pressure regulating valve 15 is used to obtain a signal pressure from the linear solenoid 16 and regulate an original pressure for control or the like, and the L / U control valve 11 and the lubrication unit 13 described above are provided downstream thereof. It is communicated. That is, the hydraulic pressure reduced by the pressure regulating valve 15 is configured to be supplied to a low hydraulic pressure supply unit such as the L / U control valve 11 or the lubrication unit 13.

  The discharge port of the mechanical hydraulic pump 14 communicates with an accumulator (pressure accumulator) 18 via a check valve 17. The check valve 17 is a one-way valve that opens when pressure oil flows from the mechanical hydraulic pump 14 toward the accumulator 18 and closes to prevent the flow of pressure oil in the opposite direction. The accumulator 18 is configured to store a piston, an elastic expansion body, and the like pressed by an elastic body in the pressure accumulating chamber in a container and store hydraulic pressure with a pressure higher than the elastic force. The accumulator 18 is configured to supply pressure oil to the high hydraulic pressure supply unit. That is, the hydraulic actuator 5 in the drive pulley 3, the hydraulic actuator 6 in the driven pulley 4, and the C1 clutch 7 are communicated with the accumulator 18. The hydraulic pressure accumulated in the accumulator 18 holds the hydraulic pressure of the high hydraulic pressure supply section when the engine is stopped. When the accumulated pressure in the accumulator 18 is insufficient, the electric hydraulic pump 9 is driven.

  A supply oil passage 19 for supplying pressure oil from the accumulator 18 to the hydraulic actuator 5 in the drive pulley 3 is provided with a supply-side electromagnetic on-off valve DSP1, and the supply-side electromagnetic on-off valve DSP1 is electrically controlled to supply oil passages. By opening and closing 19, pressure oil is supplied to the hydraulic actuator 5, and supply of pressure oil is shut off. Similarly, a supply-side electromagnetic on-off valve DSS1 is provided in a supply oil passage 20 for supplying pressure oil from the accumulator 18 to the hydraulic actuator 6 in the driven pulley 4, and this supply-side electromagnetic on-off valve DSS1 is electrically controlled. By opening and closing the supply oil passage 20, the pressure oil is supplied to the hydraulic actuator 6 and the supply of the pressure oil is shut off. Further, the supply oil passage 21 for supplying pressure oil from the accumulator 18 to the C1 clutch 7 is provided with a supply-side electromagnetic on-off valve DSC1, and the supply-side electromagnetic on-off valve DSC1 is electrically controlled to control the supply oil passage 21. By opening and closing, the pressure oil is supplied to the C1 clutch 7 and the supply of the pressure oil is shut off.

  A discharge oil passage 22 that connects the hydraulic actuator 5 in the drive pulley 3 to a drain location such as an oil pan is provided with a discharge-side electromagnetic on-off valve DSP2, and the discharge-side electromagnetic on-off valve DSP2 is electrically controlled. By opening and closing the discharge oil passage 22, the pressure oil is discharged from the hydraulic actuator 5 and the discharge of the pressure oil is blocked. Similarly, the discharge oil passage 23 for discharging the pressure oil from the hydraulic actuator 6 in the driven pulley 4 is provided with a discharge side electromagnetic on-off valve DSS2, and this discharge side electromagnetic on-off valve DSS2 is electrically controlled and discharged. By opening and closing the oil passage 23, the pressure oil is discharged from the hydraulic actuator 6, and the discharge of the pressure oil is blocked. Further, the discharge oil passage 24 for discharging the pressure oil from the C1 clutch 7 is provided with a discharge-side electromagnetic on-off valve DSC2, and the discharge-side electromagnetic on-off valve DSC2 is electrically controlled to open and close the discharge oil passage 24. Thus, the pressure oil is discharged from the C1 clutch 7 and the discharge of the pressure oil is blocked. These on-off valves are valves that are configured such that hydraulic pressure does not leak even in a closed state, and are configured by poppet valves, check valves, or the like.

That describes the structure for supplying and discharging hydraulic against high pressure supply section and the low pressure supply unit as described above. Since machine械式hydraulic pumps 14 are connected to the engine 1, if the engine 1 is rotating mechanical hydraulic pump 14 is also rotated in the same manner, it generates a hydraulic pressure. Further, an alternator 25 is connected to the engine 1 in the same manner as the mechanical hydraulic pump 14, and when the engine 1 is rotating, the alternator 25 is also rotated to generate electric power. The electric power generated by the alternator 25 is supplied to the electric motor 8 via the battery 26 so as to drive the electric motor 8.

  The engine 1 rotates in a so-called driven state in which fuel is supplied to the engine 1 and autonomously rotates, and in which the fuel supply and ignition are stopped and the vehicle Ve is forcibly rotated by the traveling inertial force. It happens in either case. That is, the mechanical hydraulic pump 14 is rotated to generate hydraulic pressure regardless of whether the engine 1 is driven or the engine brake is driven. The pressure and the amount of oil are in accordance with the specifications, rotational speed, and torque of the mechanical hydraulic pump 14. On the other hand, the hydraulic pressure generated by the mechanical hydraulic pump 14 is regulated to a predetermined low hydraulic pressure by the pressure regulating valve 15 and then supplied to the torque converter 10 via the L / U control valve 11. Supplied to the lubrication unit 13.

  On the other hand, the mechanical hydraulic pump 14 generates a hydraulic pressure corresponding to the operating (driving) state of the engine 1, so that the mechanical hydraulic pump 14 discharges during sudden acceleration or when a large engine braking force is generated. Pressure increases. The high hydraulic pressure generated in such a case is configured to push the check valve 17 open and to be supplied to the accumulator 18. Since the check valve 17 closes when the discharge pressure of the mechanical hydraulic pump 14 is lower than the hydraulic pressure in the accumulator 18, the high hydraulic pressure supplied to the accumulator 18 is stored here. The accumulator 18 stores a hydraulic pressure higher than the maximum pressure required for the continuously variable transmission mechanism 2.

  The transmission torque capacity of the continuously variable transmission mechanism 2 is controlled to a capacity capable of sufficiently transmitting the input torque, and this is set by a clamping pressure corresponding to the hydraulic pressure supplied to the hydraulic actuator 6 of the driven pulley 4. More specifically, the clamping pressure is controlled according to the required driving force required based on the accelerator opening, the throttle opening, and the like, and when the required driving force is large, it is supplied to the hydraulic actuator 6 of the driven pulley 4. The hydraulic pressure is controlled to be high. The control is performed by opening the supply-side electromagnetic on-off valve DSS 1 communicating with the hydraulic actuator 6 of the driven pulley 4 and supplying hydraulic pressure from the accumulator 18 to the hydraulic actuator 6. The opening / closing control of the supply side electromagnetic opening / closing valve DSS1 can be performed based on the target pressure or the target clamping pressure in the hydraulic actuator 6 of the driven pulley 4 and the actual hydraulic pressure in the hydraulic actuator 6. Therefore, the hydraulic actuator 6 It is preferable to provide a sensor (not shown) for detecting the actual hydraulic pressure at.

  Further, when the clamping pressure is reduced based on the reduction in the input torque to the continuously variable transmission mechanism 2, the discharge side electromagnetic on-off valve DSS 2 communicated with the hydraulic actuator 6 of the driven pulley 4 is opened. That is, the electromagnetic coil (not shown) of the discharge side electromagnetic opening / closing valve DSS2 is energized to separate the valve body from the valve seat portion and to connect the hydraulic actuator 6 to the drain portion. The energization control for the discharge side electromagnetic on-off valve DSS2 can also be performed based on the target pressure or target clamping pressure in the hydraulic actuator 6 of the driven pulley 4 and the actual hydraulic pressure in the hydraulic actuator 6.

  The gear ratio of the continuously variable transmission mechanism 2 is obtained from the shift map based on the required drive amount such as the accelerator opening and the vehicle speed V or the turbine speed. Therefore, the groove width of the drive pulley 3 is controlled so as to be the target gear ratio. The control is performed by supplying and discharging pressure oil to and from the hydraulic actuator 5 in the drive pulley 3, and specifically, by opening and closing the supply side electromagnetic on-off valve DSP1 and the discharge side electromagnetic on-off valve DSP2. . For example, when the groove width is narrowed and the belt winding radius is increased in order to upshift, the supply-side electromagnetic on-off valve DSP1 is controlled to be opened and pressure oil is supplied to the hydraulic actuator 5. On the other hand, when the groove width of the drive pulley 3 is increased and the belt winding radius is decreased so as to downshift, the discharge side electromagnetic on-off valve DSP2 is controlled to open and discharged from the hydraulic actuator 5.

  As described above, the opening / closing control of the supply-side electromagnetic on-off valve DSP1 and the discharge-side electromagnetic on-off valve DSP2 that controls the gear ratio is performed by the stroke amount of the movable sheave 3b constituting the driving pulley 3, the rotational speed of the engine 1 or the input rotation. This can be done based on the comparison result between the actual gear ratio and the target gear ratio, which is the ratio between the number and the output rotation speed, or the comparison result of the pressures of the hydraulic actuators 5 and 6 in the pulleys 3 and 4.

  In a steady running state in which the accelerator opening and the vehicle speed V are maintained substantially constant, control is performed so that the gear ratio and the clamping pressure are maintained constant. In this case, the solenoid on / off valves for the continuously variable transmission mechanism 2 are controlled to be in the OFF state, the supply oil passages 19 and 20 and the discharge oil passages 22 and 23 are closed, and the hydraulic oil is sealed in the hydraulic actuators 5 and 6. In this state, there is no leakage of hydraulic pressure from each electromagnetic on-off valve, so the hydraulic pressure stored in the accumulator 18 decreases or the hydraulic pressure is continuously supplied from the accumulator 18 to maintain the pressure of the hydraulic actuators 5 and 6. There is no need to do. Therefore, energy loss due to hydraulic pressure leakage does not occur. Note that the leakage of hydraulic pressure does not occur even when each electromagnetic on-off valve is controlled to be open.

  Further, when the vehicle Ve travels, the C1 clutch 7 is engaged to transmit torque to drive wheels (not shown). Since the C1 clutch 7 transmits a large torque required for traveling, the hydraulic pressure is supplied from the accumulator 18 to the C1 clutch 7 when the vehicle Ve travels. That is, when the vehicle Ve starts, the supply-side electromagnetic on-off valve DSC1 interposed in the supply oil passage 21 of the C1 clutch 7 is energized to control the opening thereof, and the hydraulic pressure is applied from the accumulator 18 to the C1 clutch 7. By supplying, the C1 clutch 7 is engaged. In order to avoid sudden engagement of the C1 clutch 7, it is preferable to gradually increase and decrease the engagement pressure of the C1 clutch 7 by repeatedly opening and closing the supply-side electromagnetic on-off valve DSC1 in a short time. Alternatively, it is preferable to provide an accumulator on the supply side of the C1 clutch 7 and gradually increase the engagement pressure in accordance with the characteristics of the accumulator. When the C1 clutch 7 is released, the discharge side electromagnetic opening / closing valve DSC2 is controlled to be discharged from the C1 clutch 7. Also in that case, in order to gradually release the C1 clutch 7, it is preferable to repeatedly open and close the discharge-side electromagnetic on-off valve DSC2 within a short period of time, or to gradually release pressure with an accumulator.

  The open / close valves for the C1 clutch 7 are also closed by pressing the valve body against the valve seat, as with the electromagnetic open / close valves for the continuously variable transmission mechanism 2 described above. Since this valve is a valve that does not cause substantial leakage of hydraulic pressure, the hydraulic pressure can be contained in the C1 clutch 7 and maintained in the engaged state without consuming the hydraulic pressure stored in the accumulator 18. In addition, energy loss due to hydraulic leakage can be prevented or suppressed.

  An electronic control unit (ECU) 27 for controlling the speed ratio of the continuously variable transmission mechanism 2 by controlling the on-off valves DSP1, DSS1, DSC1, DSP2, DSS2, DSC2, the engine 1, the electric motor 8, and the like. Is provided. The electronic control unit 27 is mainly composed of a microcomputer, performs calculations using input data, prestored data and programs, and outputs the calculation results as command signals to each control part. It is configured to output.

  The electronic control unit 27 includes a detection signal from the vehicle speed sensor 28 indicating the vehicle speed V, an accelerator opening signal from the accelerator opening sensor 29 that detects the depression amount of the accelerator pedal, and a throttle sensor 30 that detects the opening of the throttle. The throttle sensor signal, the actual hydraulic pressure detection signal from the hydraulic sensor 31 that detects the hydraulic pressure accumulated in the accumulator 18, and the like are input as data.

  In the shift control device for an automatic transmission mechanism according to the present invention, the hydraulic pressure generated by the mechanical hydraulic pump 14 is transferred to the accumulator 18 via the check valve 17 when the engine 1 is driven by the traveling inertia force. It is controlled so that it is supplied and accumulated. FIG. 1 shows the control flowchart. In the control example shown in FIG. 1, it is first determined whether or not the engine 1 is in a driven state driven by a traveling inertia force or the like (step S1). The determination of the driven state of the engine 1 is calculated by the electronic control unit 27 based on the vehicle speed V detected by the vehicle speed sensor 28 and the signal detected by the accelerator opening sensor 29 or the throttle sensor 30. To be judged. The calculation content is, for example, that the vehicle speed V detected by the vehicle speed sensor 28 is equal to or higher than a predetermined threshold value, and the signal detected by the accelerator opening sensor 29 or the throttle sensor 30 is equal to or lower than a predetermined threshold value. When it is determined that there is no drive request for the engine 1, it is determined that the engine 1 is in a driven state, and a positive determination is made in step S1. On the other hand, when it is determined that there is a drive request for the engine 1, it is determined negatively that the engine 1 is not in a driven state driven by the traveling inertia force. These threshold values can be obtained in advance by experiments, simulations, or the like.

  If the determination in step S1 is affirmative, that is, if it is determined that the engine 1 is in a driven state, the pressure accumulation amount of the accumulator 18 continues from or in parallel with the control in step S1. Is less than or equal to a predetermined threshold value (step S2). The pressure accumulation amount of the accumulator 18 is detected by the hydraulic pressure sensor 31 described above, and if the detected hydraulic pressure is equal to or less than a predetermined threshold, it is determined that the pressure accumulation start condition is satisfied, step S2 Is positively determined. If a positive determination is made in step S2, the pressure regulating valve 15 is controlled, and the hydraulic pressure generated by the mechanical hydraulic pump 14 is supplied to the accumulator 18 via the check valve 17 and accumulated. On the contrary, if the hydraulic pressure in the hydraulic chamber detected by the hydraulic pressure sensor 31 is larger than a predetermined threshold value, it is determined that it is not necessary or impossible to accumulate pressure, and a negative determination is made in step S2. This threshold value can be obtained in advance by experiments, simulations, or the like.

  Subsequent to the control in step S2, the belt-type continuously variable transmission mechanism 2 is upshifted to reduce the rotational speed of the engine 1, thereby reducing the rotational speed of the engine 1 (step S3). The control for relatively reducing the speed ratio of the belt-type continuously variable transmission mechanism 2 generates a drive resistance generated when the hydraulic pressure generated by the mechanical hydraulic pump 14 is accumulated in the accumulator 18, that is, an excessive engine braking force. This is control for reducing the amount of friction to be caused. Therefore, when an upshift is performed to relatively reduce the speed ratio of the belt type continuously variable transmission mechanism 2, the rotational speed of the engine 1 is decreased in conjunction with the belt type continuously variable transmission mechanism 2, that is, mechanical type. The rotational speed of the hydraulic pump 14 is reduced. Then, the drive resistance of the mechanical hydraulic pump 14 generated when accumulating the hydraulic pressure generated by the mechanical hydraulic pump 14 is reduced.

In the shift control device for an automatic transmission mechanism according to the present invention, as described above, when the engine 1 is in a driven state driven by a traveling inertia force or the like, the mechanical hydraulic pump 14 is driven to perform pressure accumulation regeneration. It is configured as follows. Further, when accumulating pressure, the driving resistance of the mechanical hydraulic pump 14 causes excessive engine braking force, so an upshift is performed to relatively reduce the gear ratio of the belt-type continuously variable transmission mechanism 2. by lowers the rotational speed of the engine 1 is controlled to reduce the driving resistance of the mechanical hydraulic pump 14 driven Sasera is by the engine 1. Then, the pressure oil discharged from the mechanical hydraulic pump 14 is supplied to the accumulator 18 via the check valve 17 and is accumulated by controlling the pressure regulating valve 15 to be closed. Therefore, it is possible to store a relatively high hydraulic pressure in the accumulator 18 without driving the electric hydraulic pump 9. Further, by upshifting the belt type continuously variable transmission mechanism 2, generation of excessive engine braking force can be suppressed or reduced, so that a drop in the vehicle speed V of the vehicle Ve can be reduced and re-acceleration can be facilitated. In addition, fuel consumption can be improved.

If a negative determination is made in step S1, the routine is temporarily terminated, assuming that the engine 1 is not in the driven state driven by the traveling inertia force. Also, if a negative determination is made in step S2, the accumulator of the accumulator 18 is greater than a predetermined threshold value, no further pressure accumulator is required or accumulator can be Na has a temporarily ends the lever routine .

In the control example described above, the driving resistance can be reduced by upshifting the belt type continuously variable transmission mechanism 2 . Machine械式drives the hydraulic pump 14 to more accurately calculate the driving resistance (friction) which occurs when performing pressure accumulation, the control to suppress or reduce the excessive engine braking force is generated by the drive resistor An example is shown in FIG.

  FIG. 2 is a control flowchart for explaining an example of the control. First, the engine 1 is in a driven state driven by a traveling inertia force, and the accumulated pressure amount of the accumulator 18 is equal to or less than a predetermined threshold value. It is determined whether or not there is (step S4). This step S4 corresponds to step S1 and step S2 shown in FIG. If the engine 1 is in a driven state and the pressure accumulation amount of the accumulator 18 is equal to or less than a predetermined threshold value, an affirmative determination is made in step S4. On the other hand, when the engine 1 is in a driving state and the accumulated pressure amount of the accumulator 18 is larger than a predetermined threshold value, a negative determination is made.

  Subsequent to or in parallel with the control in step S4, a target pressure accumulation amount to be accumulated in the accumulator 18 is calculated. Further, based on the target pressure accumulation amount and the number of revolutions of the engine 1 at the time when the target pressure accumulation amount is calculated, the driving resistance of the mechanical hydraulic pump 14 generated when the target pressure accumulation amount is accumulated in the accumulator 18, that is, excessively large. The drive resistance of the mechanical hydraulic pump 14 that is a cause of engine brake force is calculated (step S5).

Next, the gear ratio of the belt-type continuously variable transmission mechanism 2 that can reduce the braking torque corresponding to the calculated driving resistance is calculated (step S6). Then, the upshift amount calculated in step S6 is executed (step S7). This (also called friction) mechanical occurs with the driving resistance of the hydraulic pump 14 when performing pressure accumulation is because the causes of so-called excessive engine braking force, the resistance amount corresponding belt-type continuously variable transmission By making the gear ratio of the mechanism 2 relatively small, that is, by upshifting, control is performed so as to cancel out the deceleration due to the resistance.

Therefore, the engine 1 is a driven state, the resistance that occurs when performing accumulator by a mechanical hydraulic pump 14, by performing an upshift of relatively small gear ratio of the belt type continuously variable transmission mechanism 2 Since it cancels out, generation | occurrence | production of the excessive engine brake force which arises when driving the mechanical hydraulic pump 14 and accumulating can be suppressed or reduced appropriately.

If a negative determination in step S4 described above, an engine 1 is driven state and greater than a threshold pressure accumulation amount of the accumulator 18 is predetermined, it is not necessary in the accumulator, or that can not be the accumulator, and once to end the leverage of the routine.

Further, when the vehicle Ve is rapid braking, in addition to the braking by the brake, the engine braking force using friction of the engine 1, a resistor caused when performing accumulator by driving the mechanical hydraulic pump 14 It is preferable to use it positively. That is, depending on resistance of the mechanical hydraulic pump 14 with the pressure accumulator, by generating a so-called excessive engine brake force is controlled to increase the braking force. An example of the control is shown in FIG.

  FIG. 3 is a control flowchart for explaining an example of the control. First, it is determined whether or not the vehicle Ve is in a state of sudden braking (step S8). This is determined, for example, when the deceleration G of the vehicle Ve detected by the acceleration sensor 32 is equal to or greater than a predetermined threshold value. If the deceleration G detected by the acceleration sensor 32 is greater than or equal to a predetermined threshold value and it is determined that the vehicle Ve is in a state of rapid braking, an affirmative determination is made in step S8. On the other hand, if it is determined that the deceleration G is equal to or less than a predetermined threshold value, the vehicle Ve is determined to be not suddenly braked, and thus a negative determination is made. This threshold value can be obtained in advance by experiments, simulations, or the like.

Following or in parallel with the control of step S8, an upshift that relatively reduces the gear ratio of the belt type continuously variable transmission mechanism 2 is prohibited (step S9). Further, following the control of step S9, or in parallel with this, a downshift for relatively increasing the speed ratio of the belt type continuously variable transmission mechanism 2 is performed, and a line corresponding to the set speed ratio. that push adjusted to pressure. In addition, when the pressure accumulation amount of the accumulator 18 is equal to or less than a predetermined threshold value, the pressure regulating valve 15 is controlled, and the hydraulic pressure generated by the mechanical hydraulic pump 14 is passed through the check valve 17 to accumulator 18. To be accumulated (step S10). The downshift in step S10 is downshifted to a gear ratio at which the vehicle Ve can stop and restart, or to a maximum gear ratio of the belt type continuously variable transmission mechanism 2 mounted on the vehicle Ve.

  Subsequent to the control in step S10, it is determined that the gear ratio of the down-shifted belt-type continuously variable transmission mechanism 2 is equal to or greater than a predetermined gear ratio at which the vehicle can restart again (step S11). This is done by detecting the difference in the rotational speed between the driving pulley 3 and the driven pulley 4 by a rotational speed sensor (not shown). If it is determined that the gear ratio of the belt-type continuously variable transmission mechanism 2 is equal to or greater than a predetermined gear ratio at which the vehicle can restart, step S11 is positively determined. On the other hand, if it is determined that the speed ratio of the belt type continuously variable transmission mechanism 2 is not equal to or higher than a predetermined speed ratio at which the vehicle can restart again, the process returns to step S10 and can be restarted at a predetermined speed. It is controlled to downshift to a proper gear ratio.

  Following or in parallel with the control of step S11, it is determined whether or not the pressure accumulation amount of the accumulator 18 is equal to or less than a predetermined threshold value. That is, it is determined whether or not the hydraulic pressure required when the vehicle Ve stops due to sudden braking and restarts is secured in the accumulator 18 (step S12). If it is determined that the pressure accumulation amount of the accumulator 18 is equal to or less than a predetermined threshold value, an affirmative determination is made in step S12. On the contrary, if it is determined that the pressure accumulation amount of the accumulator 18 is not less than or equal to a predetermined threshold value, a negative determination is made in step S12 because the necessary pressure accumulation amount is secured.

  Subsequent to the control in step S12, the electromagnetic on-off valves DSP1 and DSS2 are closed (step S13). That is, by closing the supply side electromagnetic on-off valve DSP1 of the drive pulley 3 and the discharge side electromagnetic on-off valve DSS2 of the driven pulley 4, the speed ratio of the belt type continuously variable transmission mechanism 2 is fixed. Further, by closing the electromagnetic on-off valves DSP1 and DSS2, the pressure oil supplied from the mechanical hydraulic pump 14 is not supplied to the supply-side electromagnetic on-off valve DSP1 of the drive pulley 3, so that the accumulator 18 is more pressurized. Oil is supplied and it becomes easy to accumulate pressure.

  Therefore, in addition to the engine braking force generated by the downshift, the line pressure is set high in preparation for the case where the vehicle Ve stops and restarts, and the resistance of the mechanical hydraulic pump 14 due to pressure accumulation is Since it is added to the braking force, the deceleration G when the vehicle Ve is suddenly braked can be increased. Further, since the braking force can be increased, the stop distance required until the vehicle Ve stops by braking can be shortened.

  If a negative determination is made in step S8 described above, it is determined that the vehicle Ve is not suddenly braked, and this routine is temporarily terminated. If the determination in step S11 is negative, the routine is temporarily terminated assuming that the gear ratio suitable for the case where the vehicle Ve stops and restarts is secured. Furthermore, if a negative determination is made in step S12 described above, it is assumed that the necessary hydraulic pressure is accumulated in the accumulator 18, and this routine is once ended.

  By the way, in these control examples described above, when the engine 1 is driven by a driving inertia force or the like, and when there is a high frequency of repeating a driving request due to an accelerator operation or the like and driving independently. The frequency of pressure accumulation is increased, and the controllability of the vehicle speed V may be deteriorated. Further, when the engine 1 has a relatively low rotational speed, for example, when the engine 1 is driven near the self-supporting rotational speed, the above-described control may prevent an upshift, and the accelerator Each time ON / OFF is repeated, an excessive engine braking force is generated, and the controllability of the vehicle speed V may be deteriorated. For this reason, for example, when the number of accelerator ON / OFF operations (switching) within a predetermined time exceeds the predetermined number and there is a margin in the amount of accumulated pressure in the accumulator 18, it is preferable to control so as not to accumulate pressure. . An example of the control is shown in FIG.

Figure 4 is a control flowchart for explaining an example of the control, first, whether there are more times Misao Sakukai number of the accelerator ON / OFF is detected within a predetermined time is predetermined not Is determined (step S14). This is determined by the number of detections of the signal detected by the accelerator opening sensor 29 within a predetermined time being equal to or greater than a predetermined threshold. If it is determined Misao Sakukai number of the accelerator ON / OFF detected by the accelerator opening sensor 29 is equal to or higher than the threshold in a predetermined time period, an affirmative determination is made in step S14. On the contrary, when it Misao Sakukai number of the accelerator ON / OFF detected by the accelerator opening sensor 29 is less than the threshold value is determined within a predetermined time, as not occur disadvantages described above In step S14, a negative determination is made. These threshold values can be obtained in advance by experiments, simulations, or the like.

  Following or in parallel with the control of step S14, it is determined whether or not the engine 1 is in a driven state driven by the traveling inertia force (step S15). If the engine 1 is in the driven state, an affirmative determination is made in step S15. On the other hand, if the engine 1 is driven independently, a negative determination is made in step S15.

  Following the control of step S15, the rotational speed of the engine 1 corresponds to the drive resistance generated by the mechanical hydraulic pump 14 by upshifting to the self-sustained rotational speed of the engine 1 necessary for traveling of the vehicle Ve. It is determined whether or not the rotational speed is equal to or lower than the rotational speed to which the braking torque can be reduced (step S16). That is, it is determined whether or not the traveling state is such that the drive resistance of the mechanical hydraulic pump 14 can be offset by upshifting the transmission ratio of the belt type continuously variable transmission mechanism 2 to be relatively small. If the rotational speed of the engine 1 is equal to or lower than the rotational speed that can cancel the drive resistance generated by the mechanical hydraulic pump 14 due to the upshift, an affirmative determination is made in step S16. On the contrary, if the rotational speed of the engine 1 is larger than the rotational speed capable of canceling the drive resistance generated by the mechanical hydraulic pump 14 by the upshift, a negative determination is made in step S16.

Following or in parallel with the control in step S16, it is determined whether or not the pressure accumulation amount of the accumulator 18 is larger than a predetermined threshold value (step S17). Here, the pressure accumulation amount of the accumulator 18 is determined based on whether or not the oil pressure detected by the oil pressure sensor 31 is larger than a predetermined threshold value. The hydraulic pressure threshold value can be obtained in advance by experiments or simulations. And more specifically, the belt-type continuously variable transmission mechanism 2 of the gear ratio hydraulic capable of extent changes in the. If the pressure accumulation amount of the accumulator 18 is larger than a predetermined threshold value, an affirmative determination is made in step S17. On the contrary, if the accumulated pressure amount of the accumulator 18 is equal to or less than a predetermined threshold value, the belt type continuously variable transmission mechanism 2 cannot be shifted by the hydraulic pressure accumulated in the accumulator 18, and in step S17, Judgment is negative.

  Subsequent to the control in step S17, the pressure accumulation in the accumulator 18 by the mechanical hydraulic pump 14 is limited (step S18). That is, by not accumulating pressure on the accumulator 18, the frequency of pressure accumulation on the accumulator 18 is suppressed or reduced.

Therefore, when the accelerator ON / OFF is repeated and the engine 1 repeats the driving state / driven state, it is possible to suppress or reduce the generation of excessive engine braking force due to pressure accumulation. In addition, since excessive engine braking force can be suppressed, controllability of the vehicle speed V can be improved . That is, it is possible to suppress or reduce to thus re-accelerate the drop of excessive vehicle speed V, the it is possible to improve the fuel economy.

  If a negative determination is made in step S14 described above, this routine is temporarily terminated, assuming that there is no inconvenience due to accelerator ON / OFF switching. If the determination in step S15 is negative, the routine is temporarily terminated assuming that the engine 1 is being driven independently. Furthermore, if a negative determination is made in step S16 described above, this routine is terminated once that the driving resistance of the mechanical hydraulic pump 14 cannot be canceled by the upshift. Furthermore, if a negative determination is made in step S17 described above, it is assumed that the necessary hydraulic pressure is accumulated in the accumulator 18, and this routine is temporarily terminated.

  Here, the relationship between the above-described specific example and the present invention will be briefly described. The functional means for executing steps S1 and S15 shown in the figure corresponds to the driven state determining means in the present invention, and step S2 The functional means for executing Step S12 and Step S17 corresponds to the pressure accumulation amount detecting means in the present invention, and the functional means for executing Step S3 and Step S7 corresponds to the upshift executing means in the present invention. The functional means for executing step S5 corresponds to the drive resistance calculating means in the present invention, the functional means for executing step S6 corresponds to the upshift amount calculating means in the present invention, and the functional means for executing step S8. The means corresponds to the sudden braking determination means in the present invention, and the functional means for executing step S9 The functional means for executing step S10 corresponds to the upshift prohibiting means in the present invention, the functional means for executing downshift in the present invention, and the functional means for executing step S11 is the gear ratio detecting means in the present invention. The functional means for executing step S14 corresponds to the drive state change frequency detecting means in the present invention, and the functional means for executing step S16 corresponds to the engine speed detecting means in the present invention.

  The present invention can be applied not only to a shift control device for a belt type continuously variable transmission mechanism but also to a shift control device for a toroidal continuously variable transmission mechanism.

  DESCRIPTION OF SYMBOLS 1 ... Engine, 2 ... Automatic transmission mechanism, 14 ... Mechanical hydraulic pump, 18 ... Accumulator (pressure accumulator).

Claims (5)

An automatic transmission mechanism that shifts the power generated by the engine, a mechanical hydraulic pump that is driven by the engine to generate hydraulic pressure at a relatively low pressure, and is connected to the mechanical hydraulic pump by the mechanical hydraulic pump. And a pressure accumulator for accumulating at least a part of the generated hydraulic pressure, and the shift of the automatic transmission mechanism configured to perform control to change the rotational speed of the engine by controlling a transmission ratio of the automatic transmission mechanism. In the control device ,
The automatic transmission mechanism includes a continuously variable transmission mechanism mounted on a vehicle and capable of setting a transmission gear ratio steplessly,
A driven state determining means for determining that the driven state before SL engine is driven by such driving inertia,
A pressure accumulation amount detecting means for detecting that the pressure accumulation amount of the pressure accumulator is a predetermined value or less;
When the driven state determining means determines that the engine is in a driven state and the pressure accumulation amount detecting means detects that the pressure accumulation amount of the pressure accumulator is less than or equal to a predetermined value , the pressure accumulation calculates a target pressure accumulation amount to be accumulated in a vessel, further causes boosted hydraulic pressure generating pre Symbol mechanical hydraulic pump, accumulator executed for accumulating at least a portion of the hydraulic generating the mechanical hydraulic pump to the accumulator Means,
Based on the target pressure accumulation amount calculated by the previous SL accumulating execution means and the rotational speed of the engine at that time, generated by the machine械式hydraulic pump in case of the accumulator to the target pressure accumulation amount with respect to the accumulator Driving resistance calculating means for calculating a driving resistance of the mechanical hydraulic pump that is applied to apply braking force to the vehicle;
And Appushifu DOO amount calculating means for calculating the speed ratio of the continuously variable speed change mechanism to decrease the rotation speed of the engine so as to reduce the braking force corresponding to the driving resistance calculated by said driving resistance calculation means,
By upshift to the gear ratio calculated by the up-shift amount calculation means the transmission ratio of the continuously variable transmission mechanism, and a A Ppushifuto execution means to reduce the braking force corresponding to the drive resistance of the mechanical hydraulic pump A speed change control device for an automatic speed change mechanism. Sudden braking determination means for determining that the vehicle is being suddenly braked;
Wherein when said vehicle by the sudden braking determination hand position is the state of being suddenly braked is determined, the continuously variable transmission mechanism of the gear ratio relatively upshift inhibition for inhibiting an upshift to reduce and hand-stage,
If it is a state where the vehicle by the front Symbol sudden braking determination hand stage is abrupt braking is determined, a downshift means for relatively large speed change ratio before Symbol CVT,
Gear ratio detection means for detecting that the set gear ratio is greater than or equal to a predetermined gear ratio when the gear ratio of the continuously variable transmission mechanism is set to be relatively large by the downshift execution means ; The shift control apparatus for an automatic transmission mechanism according to claim 1, further comprising: A driving state change frequency detection means to detect that the number of times to repeat the driven state the engine and the driving state within the predetermined time period is equal to or more than the predetermined number of times,
Detecting that the rotational speed of the front SL engine, wherein less than or equal rotational speed that can offset the driving resistance is generated by the mechanical hydraulic pump by performing an upshift of relatively small gear ratio of the continuously variable transmission mechanism an engine speed detecting means to
Further comprising
Number of times to repeat the driving state and the driven state of the engine detected by said driving state change frequency detecting hand stage is equal to or greater than a predetermined number of times, and accumulating the amount of the accumulator detected by the pressure accumulation amount detecting means There a large case than the predetermined value, the shift control system for an automatic transmission mechanism according that it will not perform the hydraulic pressure of the accumulator before Symbol accumulator to claim 1, wherein. Before SL CVT structure is claimed that the groove width of the pulley belt is wound, characterized in that it is a belt-type continuously variable transmission mechanism to change by moving the movable sheave constituting the pulley by a hydraulic Item 2. The shift control device for an automatic transmission mechanism according to Item 1. Before SL downshift means to claim 2, characterized in that downshifting is set to one of the gear ratio or maximum speed ratio gear ratio the vehicle can start moving again in the continuously variable transmission configuration A shift control device for the automatic transmission mechanism described.

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